JPS59130731A - Power unit support device, driving wheel driving gear and suspension system in vehicle - Google Patents

Abstract

PURPOSE:To simplify the construction of the whole unit and make it compact by constructing a casing in a rigid body and installing suspension spring devices between said casing and a body frame. CONSTITUTION:Since both driving wheels Wf, Wf' are connected together by the casing 70 of a power unit P which is constructed in a rigid body, this casing 70 has the function of a stabilizer by which the up-down vibration of one driving wheel can be suppressed by the other driving wheel. To damp down the up-down motion of the both driving wheels, a hydraulic damper 97 is installed between each of support plate 1a, 1a' of a body frame F and each of transmission case 71, 71'. A pivot 83 is placed so as to pass through the center of gravity, while reducing the moment of inertia of the swinging system around the pivot 83. As a result, the road following capacity of the driving wheels is improved while the load shared by Neidhalt cushions Sf, Sf' is reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a power unit support, drive wheel drive, and suspension system in a vehicle equipped with a pair of left and right drive wheels.

Conventionally, in a vehicle having a pair of left and right drive wheels, such as a four-wheel vehicle, the power unit support device, the drive wheel drive device, and the suspension device are each independent. If it were possible to configure the device in an integrated manner, it would be extremely beneficial for simplifying and compacting the structure of the entire device.

The present invention was made based on such an idea, and an object of the present invention is to provide the above-mentioned device having a simple and compact structure. In order to achieve this object, the present invention +i constitutes a power unit including an engine and a pair of transmission devices that individually transmit the power of the engine to both of the driving wheels, and forms the casing of the two-wheel drive unit into a rigid body. The two-layer driving wheels are supported thereon, the casing is swingably connected to the vehicle body frame via a pivot to allow vertical movement of the two-layer driving wheels, and a suspension spring is provided between the casing and the vehicle body frame. It is characterized by being equipped with a device.

Embodiments of the present invention will be described below with reference to the drawings.

First, starting with the first embodiment shown in FIGS. 1 to 7, in FIGS. 1 to 3, the illustrated vehicle has a pair of left and right drive wheels Wf, Wf' at the front of a body frame F. A power unit P for driving the vehicle is disposed at the rear of the vehicle, and a driven wheel Fr is disposed at the rear of the vehicle.

The vehicle body frame F has support plates 1 a and 1 c' at each front end.
A pair of left and right vertical members 1, 1' that stand upright, a plurality of horizontal members 2, 3, 4, 5 that connect them in a ladder shape, and two horizontal members 3, 4 in the middle are connected. A pair of reinforcing materials 6, 6
', and three inverted U-shaped roll pars 7 connected to the front, middle and rear parts of the longitudinal members 1 and 1' to connect them.
．． 8.9, the front roll par 7, the frontmost cross member 2, and the left and right support plates 1a, ia,' are connected via a cross-shaped reinforcing member 1o, and the central roll par 8 and the rear rollper 9 are connected at their tops via a reinforcing member 11. A steering column supporting a steering handle 13 is attached to the center of the front roll par 7.

Said pair of reinforcing members 6 along the center line between both longitudinal members 1, 1'
, 6', and this fuel tank 12 is bolted to the cross member 3 and both sleeve reinforcement members 6, 6'.

A floor plate 16 is attached to the lower surface of the vehicle body frame F, and a front seat 14 for the driver and a rear seat 15 for the passenger A are installed on the upper surface of the floor plate 16, and at this time, these backrests are installed. 14. ．． 15α are arranged substantially along the center roll par 8 and the rear roll par 9, respectively.

Of course, these rollpers 8 and 9 are used by the driver and passenger A.
are preselected to a height that passes over each of the above.

In Figs. 4 to 6, the power unit P consists of an engine E and a pair of left and right belt-type automatic transmissions &rW' arranged on both sides of the rear of the engine E, and each transmission J/
, M' is equipped with a reduction gear mechanism R on the output side. These automatic transmissions M, 71/' constitute the transmission device of the present invention.

The engine E is arranged with its crankshaft 20 facing in the left-right direction of the vehicle, and has an output shaft 21 on one side of the crankshaft 20, and a primary inertia force balancing shaft 2 on the other side.
2. A pump, a drive shaft 23 and a starting morph 24 are each arranged parallel to the crankshaft 20. A generator 25 is attached to one end of the crankshaft 20, and a centrifugal automatic start clutch 26 is attached to the other end, and a forward/reverse switching device 27 is provided between the clutch 26 and the output shaft 21.

This device 27 includes a drive gear 28 fixed to the output member of the clutch 26, a relay gear 29 rotatably supported by the output shaft 21 and always in mesh with the drive gear 28, and a crankshaft 20.
A small-diameter idle gear 31 rotatably supported on an idle shaft 30 parallel to the same and always meshed with the drive gear 28, a large-diameter idle gear 32 integrally connected to the small-diameter idle gear 31, and a relay gear 29 and It is comprised of a switching gear 33 that is slidably spline-fitted to the output shaft 21 adjacent to the large-diameter idle gear 32 . The switching gear 33 is
It is connected to the output shaft 21 and can move between the forward position on the right and the reverse position on the left in FIG. A dog clutch consisting of a tongue 34 and a dog hole 35 that can engage with each other is provided on the switching gear 33 and the relay gear 29, and in the backward position, the dog clutches 34 and 35 are released and the switching gear 33 is It is designed to mesh with the large diameter idle gear 32.

Therefore, when the switching gear 33 is placed in the forward position, the crankshaft 200 rotation torque is transferred to the starting clutch 26, the drive gear 28,
The signal is transmitted to the output shaft 21 through the relay gear 29 and the switching gear 33 in order, and can be rotated in the normal direction. Furthermore, if the switching gear 33 is shifted to the reverse position, the rotational torque is transferred to the starting clutch 26, the drive gear 28, and the small diameter idle gear 31.
, the large-diameter idle gear 32 and the switching gear 33 in order to be transmitted to the output shaft 21, and this can be reversed.

An annular engagement groove 36 is provided on the outer periphery of the boss portion of the switching gear 33, and a shift fork 38 that is slidably supported on a guide shaft 37 parallel to the crankshaft 20 is installed in this groove 33.
Further, the projection 38α of the boss portion of the shift fork 38 is engaged with the cam groove 39α of the shift drum 39, which is disposed parallel to the guide shaft 37. The shift drum 39 has a shift lever 40 fixed to one end thereof.
When the cam groove 39 is rotated in one direction or in the middle direction, the cam groove 39
The switching gear 33 can be shifted to the forward position or the backward position by displacing the shift fork 38 to the right or left by the guiding action of α.

The -order inertia force balancing shaft 22 is connected to drive gears 41 having the same diameter.
The crankshaft 20 is also rotated synchronously via the driven gear 42. This balance shaft 220 weight 22α is connected to the crankshaft 2
A pair of crank webs 20. which face each other when approaching zero. ．． Although the weight 22a is provided at a position where it enters between the weights 20a and 20a, the primary inertia force balancing effect of the engine E by this weight 22a is well known, so a description thereof will be omitted.

The pump drive shaft 23 is driven by the crankshaft 20 via a chain transmission 43. A lubricating oil pump 44 is connected to one end of the pump drive shaft 23, and a cooling water pump is connected to the other end, and the water pump 45 can be easily attached and detached as follows.

That is, a rotary shaft 47 having an impeller 46 of the water pump 450 is connected to the pump drive shaft 23 via a removable joint 48, and an engine housing 49 that supports the rotary shaft 47 and houses the impeller 46 is It is fixed to the crankcase 50 of the engine E with bolts 51. Therefore, by removing the bolts 51, the water pump 45 can be easily taken out from the engine E, which is convenient for maintenance.

Incidentally, when the engine E is of the air-cooled type, the water pump 45 is removed in this way, and an appropriate blind cover is applied to the opening of the crankcase 50 after the engine housing 49.

As shown in FIGS. 5A and 5B, a signal protrusion 52 of an ignition pulser is provided on the outer peripheral surface of the rotor 25α of the generator 25.
is protruding, and the pink up coil 5 of the ignition pulsar
3, its base plate 53a is attached to the crankcase 5 so as to face the turning path of the signal protrusion 52 with a certain gap therebetween.
It is fixed to a fixed support base 54 in 0 with bolts 55. In order to facilitate position adjustment and attachment/detachment of the pink amplifier coil 53, a working window 56 is provided in the end wall of the crankcase 50 facing the pickup coil 53, and this window 56 is normally closed by a camp 57. .

The pair of belt type automatic transmissions 7V and M' are connected to both ends of the output shaft 210 of the engine E and left and right drive wheels Wf.

F f/ is arranged so as to be connected to each other. Therefore, both driving wheels Wf and +7"f' are connected in parallel to the output shaft 21 via automatic transmissions /S/ and M', respectively.

Since the belt type automatic transmissions M and iW' have the same structure, only the structure of the one M will be explained.

A variable diameter drive pulley 58 is attached to the end of the output shaft 21, and a variable diameter driven pulley 59 is attached to the driven shaft 61, which is the input shaft of the reduction gear mechanism R.
B, the endless belt 60 is tensioned between 59 and 59; The driving pulley 58 includes a centrifugal mechanism 62 that operates to increase its effective diameter as its rotational speed increases, while the driven pulley 59 includes a spring 63 that constantly operates to increase its effective diameter. Due to the interaction between the centrifugal mechanism 62 and the spring 63, the gear ratio between the output shaft 21 and the driven shaft 61 is automatically reduced as the rotational speed of the output shaft 210 increases.

A wheel drive shaft 65 is provided at the outer end of the output shaft 64 of the reduction gear mechanism H.
is spline-coupled, and further to this wheel drive shaft 65,
An axle 67 fixed to a hub 66 of the drive wheel ff is connected via a constant velocity joint 68. Therefore, the power that has been shifted and transmitted to the driven shaft 61 is appropriately torque amplified by the reduction gear mechanism R, and then transmitted to the axle shaft 67 via the wheel drive shaft 65 and the constant velocity joint 68 to drive the drive wheel Wf. do.

Since the left and right driving wheels Wf, Wf' are connected in parallel to the output shaft 21 via such automatic transmissions Jf, M', both driving wheels Wf are connected in parallel due to turning of the vehicle.

When a rotational speed difference occurs in Iff', a difference occurs in the gear ratios of both automatic transmissions AI and M', and as a result,
The output torque of the output shaft 21 is distributed to both driving wheels Wf, Wf' according to their rotational speeds. That is, automatic transmission M
, M' each perform a normal speed change function, and can also work together to perform a differential function.

The casing 70 of the power unit P includes a crankcase 50 that accommodates and supports the crankshaft 20, output shaft 21, etc. of the engine E, and an automatic transmission M that extends rearward from both left and right ends of the crankcase 50.

A pair of mission cases 71°71 that accommodate and support M/wo
' are integrally connected to form a rigid body, and both transmission cases 71, 71'&'! , are arranged substantially horizontally so as to sandwich the front end portion of the vehicle body frame p from the left and right sides. In this way, the space between the two Mitsubishi Y cases 71° and 71' can be effectively used as body space, making the vehicle more compact and contributing to lowering the center of gravity of the knocker unit P. .

Crank case 50 and each transmission case 71°71'
There is a partition wall 72 between them that partitions them in an oil-tight manner.
, M' are provided with partition walls 73 that oil-tightly partition the speed change mechanism including the two boots IJ 58, 59 and the reduction gear mechanism R, and as a lubrication method, each automatic transmission M, rW.
A dry type is used for the transmission mechanism ', and a wet type is used for the reduction gear mechanism R.

The casing TO is divided into several blocks and cast as follows. That is, in the central part of the crankcase 50, in the intermediate part between the central part and each transmission case 71° 71', and in the central part of each mission case 71° 71', it is perpendicular to the axis of the crankshaft 20. The blocks thus divided are called first to sixth blocks 70□ to 706 from the left in FIG. These blocks 70
1 to 706 are bolted together between adjacent ones.

Support brackets 74 to 77 are integrally protruded from the outer surfaces of the second to fifth blocks 702 to 705, respectively, and support camps 79 are connected to these support brackets 74 to 77 via through bolts 78, respectively. - 82, there is a single pivot shaft 8 disposed parallel to the crankshaft 20 in order to connect the power unit P to the vehicle body frame F.
3 is held in place. At that time, each support bracket 74 to 77
The support surfaces of the support camps 79 to 82 are each formed into a semicircular shape that is easy to process and can be brought into close contact with the circumferential surface of the pivot shaft 830, and each through bolt 78 is formed in order to position and securely fix the pivot shaft 83 to the casing 70. The pivot shaft 83 is passed through. Thus, the second to fifth blocks 70□~
705 are also connected to each other by a pivot 83, increasing the strength of the connection.

Furthermore, each set of support brackets and camp γ4°79
;75,80;76.81;77.82 mating surfaces are mutually
・The phase is shifted in the circumferential direction of the pivot shaft 83. In this way, the relatively weak portions of the support brackets 74 to 77 and the plurality of through bolts 78 are not biased in one direction, and the pivot shaft 83 can be firmly supported in all directions.

The pivot 83 supports the support bracket 74°770 in the bilateral position.
Inside, a pair of left and right suspension spring devices 5f, 5
The left and right support plates 1a, 1 of the vehicle body frame F are connected via f'.
Supported by α′. In the illustrated example, suspension spring devices Sf, Sj
' are constructed in the Neidhard type and have the same structure, so only the one on the left Sf will be explained. As shown in FIG. 7, this suspension spring device Sf has a basic shape of hexagonal cross section Housing 9o with spring chamber 91
The basic shape has a hexagonal cross-sectional shape and the spring chamber 9
1, and six cylindrical rubber springs 93 filled between the housing 9o and the spring actuating body 92 in the hole of the spring chamber 91.
2 is fixed to the pivot shaft 83 by multi-face fitting or spline fitting. A mounting flange 94 is integrally formed on the outer circumferential surface of the housing 9° and projects over half the circumference thereof.

On the other hand, a semicircular support recess 95 opening toward the front is formed in the support plates 1α, 1α′ of the vehicle body frame F, and the housing 90 is fitted into the recess 95 so that the mounting flange 94 is attached to the support plate. 1α and 1a' with a plurality of bolts 96.

Thus, the power unit P serves as the left and right driving wheels Wf.

When Wf' swings around the pivot shaft 83 as Wf' moves up and down, the spring actuating body 92 rotates relative to the housing 90 and applies compressive deformation to all the rubber springs 93 at the same time. Drive wheels Wf, Wf due to the repulsive force of the rubber spring 93
' is suspended elastically. By the way, power unit P
As described above, the casing 70 constitutes a rigid body and connects the two driving wheels Wf, jVf', so that it has a stabilizer function that suppresses the vertical vibration of one driving wheel by the other driving wheel. It turns out.

In order to damp the vertical motion of both driving wheels If, Wf', a hydraulic damper 97 is interposed between each of the support plates 1α, 1α' of the vehicle body frame F and the transmission case 71, 71'.

The pivot shaft 83 is arranged to pass through the center of gravity of the power unit P. In this way, the moment of inertia of the swing system around the pivot shaft 83 consisting of the drive wheels Wf, Ff' and the power unit P can be significantly reduced, and as a result, the road followability of the drive wheels Wf, Wf' is improved, and The load burden on the Neidhardt spring devices Sf, Sf is reduced.

Furthermore, in order to reduce the moment of inertia, in the illustrated example, the balancing shaft 22, the starting motor 24, and the water pump 45, which are relatively heavy, are connected to the drive wheel Wf.

It is placed at the front of engine E to balance the weight of rv f/. Note that arranging the water pump 45 at the front of the engine E is convenient because its maintenance can be performed without being obstructed by the vehicle body frame F.

A support tube 100 surrounding the wheel drive shaft 65 is integrally formed on the outer surface of each mission case 71, 71', and an outer tube 101 rotatably supported by this support tube 100 includes:
A knuckle 102 rotatably supporting the hub 66 of the corresponding drive wheel F f '+ F f ' is connected via a pair of king pins 103 coaxially arranged across the swing center of the constant velocity joint 68, Further, the knuckle 102 is connected to the steering handle 13 via a steering mechanism (not shown).

Therefore, by rotating the steering handle 130 to rotate the knuckle 102 around the king pin 103, the driving wheels If and Wf' can be turned.

Further, the knuckle 102 has a corresponding drive wheel Wf.

A bank plate 104 of a brake device B (drum type in the illustrated example) of y f/ is fixed, and this back plate 11
In order to suppress the rotation of the torque rod, a restraining arm 105 is provided that protrudes from the outer surface of the outer cylinder 101.

It is connected to the vehicle body frame F via 106. Therefore, during braking, the braking torque acting on the back play) 104 is the knuckle 102, the outer cylinder 1o1, and the torque rod 106.
It is supported by the vehicle body frame FK via. In addition, when the power unit P swings around the pivot 83, the drive wheels Wf, Wf
knuckle 1 so that proper alignment of ' is maintained
02 Relative rotational displacement between the outer cylinder 101 and the support cylinder 100- in a connected relationship is allowed.

A rear fork 111 is pivotally attached to the rear end of the vehicle body frame F via a pivot 11Q so as to be able to swing vertically, and the driven wheel Wr is pivotally supported at the rear end of the rear fork 111. In order to suspend the rear fork 111, a spring device Sr having the same structure as the Neidhardt type spring device Sf is installed between the pivot shaft 110 and the rear fork 111.
is interposed.

Further, a hydraulic damper 112 is interposed between the rear fork 111 and the vehicle body frame 1 to damp the vertical movement of the driven wheel Wγ.

FIG. 8 shows a second embodiment of the present invention. To explain only the differences from the previous embodiment, the left and right automatic transmission i
Input shaft 120 to which drive pulley 58 of W HM' is attached
, 120' are separated from the output shaft 21 of the engine E,
It is disposed adjacent to and coaxially with both ends of the crankshaft 200, and the input shaft 120, 120' and the output shaft 21 are connected via a driving gear 121 and a driven gear 122, respectively.

The input shaft 120 of the casing 70 of the power unit P
．． The part surrounding 120' is a rectangular cylindrical pivot 183.18
3', and these pivot shafts 183° and 183/ are supported by the vehicle body frame F via Neidhard type suspension spring devices Sf and Sf'. Thus, the center of swing of the power unit P is located at or near the center of the crankshaft 20. In this way, rotational vibrations caused by torque fluctuations of the engine E can be effectively absorbed by the Neidhardt spring devices Sf, Sf'. The rest of the structure is the same as that of the previous embodiment, so in FIG. 8, the same reference numerals are given to the parts corresponding to those of the previous embodiment.

As described above, according to the present invention, a power unit is constituted by an engine and a pair of transmission devices that individually transmit the power of the engine to a pair of left and right drive wheels, and the casing of the power unit is formed into a rigid body. The casing is swingably connected to the vehicle body frame via a pivot shaft to support both of the driving wheels, and the casing is swingably connected to the vehicle body frame via a pivot to allow vertical movement of the both driving wheels, and a suspension spring device is interposed between the casing and the vehicle body frame. Since the casing of the power unit is equipped with a swing arm that suspends the drive wheel, it can swing as the drive wheel moves up and down, so there is no need to provide a special swing arm. Since it can also suppress the vibration of each drive wheel, there is no need to provide a special stabilizer, and the power unit can be supported and both drive wheels can be suspended using a common pivot and suspension spring device. As a result, the structure of the entire device can be simplified and compacted.

The suspension spring device is not limited to the Neidhard type as in the above embodiment, but may be a telescopic type consisting of a coil spring interposed between a swinging arm fixed to the pivot and the vehicle body frame, for example. It can also be configured as

[Brief explanation of the drawing]

1 to 7 show a first embodiment of the present invention, in which FIG. 1 is a perspective view of the separated vehicle body frame and power unit, and FIGS. 2 and 3 are plan views of the same vehicle. and a side view, FIG. 4 is a side view of the power unit, and FIG. 5 is a side view of the power unit.
5A is an enlarged longitudinal sectional plan view of the engine part of the same power unit, FIG. 5B is a sectional view taken along the line VB-VB of FIG. 5A, and FIG. 6 is a power transmission system of the engine. A side view, FIG. 7 is an enlarged sectional view taken along the line ■--■ in FIG. 5, and FIG. 8 is a longitudinal sectional plan view of a main part of a power unit showing a second embodiment of the present invention. E...engine, F...body frame, M, -M/
... Automatic transmission constituting the transmission device, P... Power unit, Sf, Sf/... Suspension spring device, Wf, W
f/... Drive wheel, 70... Casing, 83, 183, 183'.
...Axis patent applicant Honda Motor Co., Ltd.

Claims (1)

[Claims] In a vehicle equipped with a pair of left and right drive wheels, an engine and
A power unit is constituted by a pair of transmission devices that transmit the power of the engine to each of the two driving wheels, and the casing of this power unit is formed into a rigid body and supports the two driving wheels. Power unit support and drive wheel drive in a vehicle, wherein the casing is swingably connected to a vehicle body frame via a pivot to allow vertical movement, and a suspension spring device is interposed between the casing and the vehicle body frame; Suspension system.